Cone crusher



Oct. 11, 1938. H; F. CAMPBELL CONE CRUSHER Filed Dec. 5, 1955 2 Sheets-Sheet l INVENTOR )W 27 BY W, fimwa ATTORNEYS v Oct. 11, 1938. H. F. CAMPBELL CONE CRUSHER Filed Dec. 3, 1935 2 Sheets-Sheet 2 'IIIHIIIH I I YINVENTOR ATTORNEYS Patented Oct. 11, 1938 UNITED STATES PATENT OFFICE CONE CRUSHER Application December 3, 1935, Serial No. 52,645

1 Claim.

This invention relates to crushing equipment, and more particularly to machines adapted to crush such material as ore or stone.

The principal object of this invention is to pro- 5 vide relatively inexpensive crushing apparatus which is economical in operation and which pro duces a highly uniform crushed product.

The above objects are attained according to this invention by the provision of a crusher of the l so-called cone gyratory type wherein a crushing member or head is caused to gyrate within a surrounding wall, and the material is crushed in a tapering cavity between the head and the wall by the gyration of the head. Gyratory crush- 75 ers of this general type are well known in the art.

In my copending application Serial No. 40,368, filed September 13, 1935, there is disclosed a gymtory type of crusher in which the crushing head is supported by a rotating eccentric sleeve 20 mounted on a vertical shaft for creating the gyratory motion. The present invention contemplates the use of an eccentric sleeve of this type constructed to locate the axis of gyration at a point above, or near the top of, the crushing 25 head.

The invention will be better understood from the following description of a specific embodiment and the accompanying drawings, of which:

Fig. 1 illustrates a front elevation, mostly in 30 section, of a crushing machine embodying this invention;

Fig. 2 illustrates a top view of the machine partially broken away; and

Fig. 3 is a side elevation of the same machine.

35 The machine is constructed on a frame 10, the outline of which is generally cylindrical in form. The frame will ordinarily be made of a tough metal and provided with webs at appropriate places, as shown in Fig. 1, to provide strength 40 and rigidity. Centrally located within the frame and rigidly supported by radial webbing is a sleeve it into which is force-fitted a vertical shaft l2. An eccentric sleeve l3 having inner bearing surfaces M and I5 and outer bearing surfaces l6 and I1, preferably of Babbitt metal, is mounted on the shaft l2. The use of double bearing surfaces on each circumference of the eccentric permits the use of greater total bearing surface than if single cylindrical bearing surfaces were used, becausefor any given size of crushing head (described hereinafter) the lower one of each double bearing may have a greater diameter than the upper one. The eccentric sleeve I3 is 55 supported above the frame sleeve H by a roller step bearing l8, comprising rollers l9 and roller guides 20 and 2|.

Mounted on the outer bearings I6 and I I of the eccentric is a crushing head 22, approximately conical in shape. The head is supported verti- 5 cally on a roller step bearing 23 which is supported by a collar 24 rested on a supporting ledge of the eccentric sleeve. The head is strengthened by a number of vertical radial webs 25. A jacket 26, providing the crushingsurface, or wall, of the head, is placed snugly over the head 22 and firmly fastened by a nut 21 threaded on a stud 28 which projects from the head member 22 upward through a hole in the jacket. The diameter at the lower end, or skirt, of the head, includingv the jacket, may conveniently be about 60 inches. overhanging and surrounding the crushing head is a heavy mantle 29 supported by a solid ring 30 which is provided with a flange 3! having an annular recess 32 which registers with, and is supported by, an annular protuberance 33 of a flange 34 integral with the frame It]. The band 39 is clamped down to the flange 34 by a number of studs 35 (Figs. 2 and 3) extending through the flanges 3| and 34 at intervals. These studs are fastened below the flange 34 in a manner which will be described hereinafter. The outer circumferential wall 36 of the mantle is in the form of a cylinder which fits within the band 30. The in-- ner wall 31 of the mantle is approximately in the form of a frustum of a cone of which the apex is at the top. A horizontal wall ll joins walls and 31 at the top. An inner jacket 38 is tightly fitted within the conical wall 3'! and securely held by any suitable means such as screws (not 35 shown).

Means is provided for adjusting the height of the mantle relative to the frame and to the crushing head 22. This means comprises a number of vertical studs 39 the lower ends of which 40 are tightly threaded into tapped holes 49 provided at spaced intervals around the flange 3!. Directly over each of the tapped holes 48 and integral with the walls 36 and 4| are a number of horizontally bifurcated lugs 42 provided with 45 holes through which the upper ends of the studs 39 easily slide. These lugs are reinforced by means of radial webs 89. A regulating nut 43 is threaded on each stud between the bifurcated portions of the associated lug 5.2 for the purpose of regulating the vertical position of the mantle. For convenience in making the adjustment each of the nuts 43 is provided with sprocket teeth 44 which engage with a suitable endless sprocket chain 45. Movement of this chain turns all the regulating nuts 43 simultaneously in the same di-. rection, thereby uniformly raising or lowering the entire periphery of the mantle.

To facilitate this adjustment the solid band 30 is provided, at its inner periphery adjacent the mantle walls 36, with a series of wedge shaped pockets 13 formed within pocket housings 14, spaced around the circumference of the band. Each of these pockets contains a wedge 15 positioned between the walls of the pocket and the mantle wall 36. A bolt 16, positioned by its outer head 1! and by a thrust collar 18 within the pocket, is threaded into a tapped hole in the wedge. The band 30 is locked to the mantle wall 36 by turning bolts 16 to force the wedge into closer contact between wall 36 and the wall of the pocket. When the height of the mantle is to be adjusted, the wedges 15 of the band 30 are first loosened, after which the mantle may be readily raised or lowered. When the proper adjustment is had the wedges are then tightened again.

A funnel-shaped feed hopper 46, into which is fed the material to be crushed, is fastened to the upper rim of the mantle by bolts 41.

For the purpose of gyrating the crushing head there is fastened to a lower flange 48 of the eccentric l3, by bolts 49, a bevel ring gear 50 adapted to be driven by a bevel pinion i fastened to a drive shaft 52. The drive shaft and pinion are carried by a housing member 53 having a webbed flange 54 at the inner end and a straight flange 55 at the outer end. The housing 53 is held within a larger housing 56 integral with the main frame ill by forcing the flange 54 within a restricted portion of housing 56 and bolting flange 55 to a corresponding flange 51 by bolts 58.

The drive shaft 52 is mounted in the housing 53 by a roller bearing 59 near the inner end, and a ball thrust bearing 60 near the outer end. The outer portion of the roller casing of bearing 59 is driven within the end of housing 53 and the inner portion of the casing is forced onto the shaft 52. The ball race of bearing 60 is held in place by a cover plate 6| having a cylindrical portion 62 which holds the outer part of the ball race in a recess in the housing, and by lock nuts 63 which lock the inner part of the ball race in position. The cover plate 6| is provided with a central hole to permit the shaft to pass through, and is fastened over the open end of housing 53 by bolts 64.

This arrangement of the drive shaft housing keeps dust and grit away from the pinion and drive shaft bearing, and also permits the entire drive shaft assembly to be removed for repairs or inspection. To aid in keeping dust away from the bearings and gears there is fastened to the under part of the frame an annular ring 69 of a material such as bronze, having a Z-shaped cross section, which makes contact between circular lips and II integral with the under side of the head. This also acts as an oil retaining ring for an oil system which is not illustrated.

In operation, the drive shaft 52 is rotated by an external source of power (not shown) thereby causing the eccentric sleeve I3 to rotate on shaft l2. The rotation of the eccentric causes the crushing head 22 to gyrate; and the axis of the gyration is a point 0 (Fig. 1) which is approximately at the top of the crushing head and is at the intersection of the longitudinal axes of the shaft i2 and of the eccentric sleeve l3. In Fig. 1 line a is the center line or axis of shaft l2 and of the inner eccentric bearing; and line b is the axis of the outer eccentric bearing, and of the crushing head, in the position shown, wherein the head is nearer to the right hand side of the mantle. When the eccentric is rotated 180 from the position shown in Fig. 1, however, the gymtion causes the crushing head to assume the position indicated by the broken line 65, in which position the head is nearer the left side of the mantle. The axis of the head and of the eccentric in this latter position is indicated by the broken line 0. It is evident that for each rotation of the eccentric the point of closest proximity of the head to the mantle jacket sweeps through the entire 360 degrees of the mantle cir cumference.

It is observed that the surface of the mantle jacket 38 curves outwardly slightly at the lower portion, or skirt, thereof to become practically parallel with the outer surface of the crushing head. The angle which the mantle surface makes with the vertical is preferably approximately 45 degrees at the lower portion thereof, but at the upper 70 or 80 percent of this surface this angle decreases. This shape provides a very gradual downward taper of the crushing cavity walls; and the spacing between the walls of the crushing cavity for some distance from the lower end is substantially uniform. This distance of substantially parallel spacing at the bottom is preferably about 30 percent of the cavity depth; and the parallel walls of this region cause the total cross section area to increase toward the bottom. In any event it is desirable that the total cross sectional area shall not decrease toward the bottom.

Let us consider, for the moment, the "movement of the portion of the head adjacent some one part of the inner mantle wall, for example, that portion of the head adjacent the portion 61 of the mantle wall, which is shown at the extreme right in Fig. 1. When the head is in the position indicated by the broken line 65 it is in its most retracted position, and is somewhat lowered, with reference to the mantle wall portion 61. Then. while the eccentric rotates 180 degrees the head approaches the wall portion 61 with an upward component of motion until it reaches the position shown in full lines, at which it is in closest proximity to the wall portion 61. Then, when the eccentric continues to rotate through another 180 degrees the head is retracted from wall portion 61 with a downward component of motion until the head returns again to the position shown by the broken line 65. The action just described takes place successively with reference to succeeding portions of the inner mantle wall, throughout its 360 periphery.

The material to be crushed is fed into the hopper 46, from where it drops onto the crushing head and starts to slide down the outwardly slanting wall thereof. After the material has slid down a short distance, the larger lumps or masses of the material are crushed into smaller masses by the impact created when these lumps are caught between the crushing head wall and the inner wall of the mantle jacket, as the head approaches a portion of the mantle wall.

When the head retracts after having delivered the impact, the material continues to slip down and spread out on the flaring wall of the head along a course bounded by the adjacent head and mantle walls, until another impact is delivered by the head. After each succeeding impact the crushed material becomes smaller and slides along and spreads out into an area of the tapered arsaaos cavity 88 having a smaller spacing between its walls.

The final size of the crushed product is determined by the spacing between the walls at the lower end of the crushing cavity at 88, when the head is in its position closest to the mantle. The

substantially uniform spacing between the walls of the crushing cavity at and near 88 facilitates the ejection of the crushed material and tends to prevent clogging. The ejected material drops into a pit below the crushing head.

From'the foregoing, it is apparent that one impact is delivered against each portion of the mantle for every revolution of the eccentric sleeve l3. It has been found that in the type of machine described an eccentric speed of about 350 revolutions per minute results'in a smooth sliding and crushing action and delivers a very uniform product. The yield at this speed is also very satisfactory.

The size of the crushed product can be regulated by raising or lowering the mantle by means of the sprocket nuts 48, thereby increasing or decreasing the cross section of the crushing cavity.

To take care of'uncrushable material, such as iron, which might find its way into the crushing cavity there is provided means for permitting the mantle to be lifted when the crushing head strikes'such material. This means is the arrangement for fastening bolts under flange 84. The fastening arrangement comprises triangular prisms I9 and 88, (cut of! somewhat at the lower edges) having a right angle, and a frustum of a triangular prism 8|. The prism 8| is centrally tapped to receive the bolt 85, as shown. The prisms I8 and 88 are positioned so that one side of each lies against the under surface of flange 34 and the hypotenuses register with the equal surfaces 82 and 88 respectively of prism 8|. The prisms 19 and 88 are held in position by spring heads 84 and 85 held by stay-bolts 86, as shown. Springs 81 and 88 are held in compression, in recesses, between each spring head and the end face oi the adjacent prism.

When a piece of uncrushable material enters the crushing cavity, the impact of the crushing head on it causes the mantle to rise. when the mantle rises the prism 8| is pulled upward by the bolt 88, and the surfaces 82 and 88 slide on the surfaces of prisms I8 and 88 and push these latter two prisms apart against the compression of springs 81 and 88. When the uncrushable material has passed through, the mantle is drawn down into the position again by its own weight and by the action of the springs.

The construction of the crusher is simple, rigid, durable, and inexpensive. The central stud shaft i2 is strongly supported and still against ilexure in service. The crushing reaction is transmitted partly to the bearing surfaces of the eccentric, but the component of the various loads is delivered largely to the roller thrust bearing l8. Hence, the load is delivered to a relatively very low point on shaft l2. All of the parts are permanently dust-tight and accessible for thorough lubrication. The pinion drive is easily disconnected and removed for inspection, replacement and repair, without exposing any of the interior driving mechanism to the dust laden air of the discharge chamber,

This is a continuation-in-part of my co-pendlng application Serial No. 40,368, filed September 13, 1935.

I claim:

In a crusher, a casing supporting an outwardly and downwardly flaring mantle, a cooperating crushing head outwardly and downwardly flared to work under said mantle and adapted to exert an upward and outward crushing force at an angle midway between the vertical and horizontal, a vertical shaft, an eccentric on said shaft having a vertical thrust bearing rotatably carrying said head, said eccentric forming the sole support for said head, means for rotating said eccentric to give the head a gyratory crushing motion upward under the mantle around a center above the cooperating crushing surfaces of the head and mantle, and a bearing below said eccentric on said frame directly rotatably supporting said eccentric from said frame in the lines of mean reaction of the crushing forces between said surfaces.

HERBERT F. CAMPBELL. 

